Horizontal gyratory roll crusher



Jan. 15, 1952 c. A. ADAMS HORIZONTAL GYRATORY ROLL CRUSHER 2 SHEETS-SHEET 1 Filed June 27, 1946 3+ 1/ rlcfi. 50 14 a 45 INVENTQR CHARLES ,4. ADAMS ATTORNEYS Ill ///1///// 28 Jan. 15, 1952 c. A. ADAMS 2,582,734

HORIZONTAL GYRATORY ROLL CRUSHER Filed June 27, 1946 2 SHEETS-SHEET 2 LOCUS "0F AXIS 0F DRUM l2 INVENTOR CHARI. E6 A. ADAMS BY Z z 2 ATTORNEYS.

Patented Jan- 15, 1952 UNITED STATES PATENT OFFICE HORIZONTAL GYRATORY ROLL CRUSHER Charles A. Adams, Monticello, N. Y.

Application June 27, 1946, Serial No. 679,665

8 Claims.

My invention relates to crushers and in particular to gyrocentric machines for crushing rocks, ores, slag, and other crystalline materials.

In so-called horizontal gyrating rock-crushing machinery, it has been customary to feed the material to be crushed into a somewhat funnelshaped passage between a relatively fixed crushing jaw and a gyrating or eccentrically moving crusher drum. The funnel-shaped passage has been defined by the gradual convergence of the generally cylindrical periphery of the crusher drum and of the arcuate surface of the crushing-jaw plate. Power requirements for operating devices of this construction have been great, principally because of the phenomenon known as choking. This phenomenon takes place at points of close adjacency of the drum and the jaw plate, due to an inability of finely crushed elements to free themselves so as to permit the admission of further charges of partially crushed material. The choking phenomenon has caused undue wear of parts and frequent breakage.

It is, accordingly, an object of my invention to provide a crushing machine having improved features of economy of operation.

It is also an object to provide a crushing device in which the power supplied is utilized substantially only for crushing purposes.

It is a further object to provide a drum-type crushing device in which, for the life of the drum, wear of the crushing surfaces is more evenly distributed.

It is a more specific object to provide a drumtype crusher in which motion of the crusher drum is substantially only eccentric in nature and in which the amount of rotational motion of said drum is a more direct reflection of the magnitude of the crushing load sustained.

Other objects and various further features of novelty and invention will appear from a reading of the following specification in conjunction with the accompanying drawings, in which:

Fig. 1 is a perspective view of a crushing machine incorporating features of the invention;

Fig. 2 is a cross-sectional view of the crusher of Fig. 1, taken transversely and at substantially the midpoint of the drive shaft;

Fig. 3 is a cross-sectional view taken substantially in the plane 3-3 of Fig. 2;

Fig. 4 is a fragmentary cross-sectional view taken substantially in the horizontal plane including the main rotational. axis of Fig. 1, as taken in the plane 4-4 of Fig. 2;

Fig. 5 is an isometric view of parts of the device shown in the foregoing figures; and

Figs. 6 and 'l are constructional diagrams illustrating a method of developing crushing surfaces in accordance with the invention.

Broadly speaking, my invention seeks to provide improved operating efliciency in a gravityfed machine in which crushing action is effected by two tunnelling members moving relatively to each other. The improved efliciency results from employment of crushing surfaces making a relatively wide included angle (approximately the,

angle of nip for the material to be crushed) with each other, except in the region of finest crushing action, where the included angle is substantially less than the angle of nip. In the region of coarse crushing, the included angle is preferably such as to produce a crush with an upward breaking thrust, while in the fine-crush zone the relatively narrow included angle is preferably as wide as possible without producing substantial upward breaking thrust. In the specific form to be described, the crusher is a horizontal roll or drum, eccentrically gyrated between adjustable jaw plates, whereby crushing may be efiected alternately on opposite sides of said drum in an up-crushing zone and in a down-crushing zone. Each jaw plate has a complex crushing surface characterized by two generally arcuate elements which define a fine-crush region and a coarsecrush region. The relative size of the fine-crush surface with respect to crusher-drum diameter and with respect to the effective area of the coarse-crush surface is preferably such that with the roll retraction following each crushing stroke the finely crushed material may be completely discharged, thus preventing attainment of choking conditions in the fine-crush region.

Referring to the drawings, my invention is shown in application to a horizontal gyrating roll crusher having a frame 5 including side frame members 6 and I. These members are reinforced as at 8 to provide rugged outboard bearings 9l 0 for the main eccentrically gyrated crusher drum. In the form shown, the crusher drum comprises a mantle or crushing portion ll carried on an annular drum or support member I2. The drum I2 is in turn supported as by sleeve means l3 on eccentric means in the form of a cylindrical surface M of the main drive shaft IS; the axis of the cylindrical surface I4 is displaced from the axis of the shaft l5 so as to impart an eccentrical throw to the crushing mantle i I for crushing purposes.

The crushing action occurs between the eccentrically gyrated crushing drum and the crushing-plate surfaces of a pair of swing jaws Iii-47 tracting throw of the crushing mantle ll.

assays;

pivotally mounted on the frame members 6 and I to either side of the drum l2. Side plates l8 and it are mounted as by bolts 20 to the frame members 6 and I to form a close but free fit with the ends of the crushing Jaws and of the crushing-drum 'mantle ll, thereby defining the crushtion of the walls of the crushing chamber. In

the form shown, this novel construction is applied to the crushing jaws l6 and I! to produce a double arcing of their crushing surfaces. As indicated above, this double arcing is for the purpose of' separately defining within the crushing chamber a coarse-crush region 22 and a finecrush region 23, the contents of the latter being substantially completely discharged for each re- The coarse-crush region is preferably defined by two outwardly divergent surfaces forwhich the included angle is substantially the angle of nip for the material to be crushed; in the fine-crush region this included angle of divergence is materially less.

Due to the necessarily arcuate surface of the mantle II, the diverging walls of the crushing chamber in both the fine and coarse-crush rethat suitable fineness of product may be obtained by spacing the crushing members 24 and 25 by an element of length x, and that the region of fine crushing is defined'by an included angle of the region extending a length 3.1:. Further up, the coarse-crushing region is defined by an included angle'of 31, the assumed angle of nip for the material to be crushed (for most ores, stone, gravel, etc., the angle of nip is generally conceded to be 31 or less); in the form shown, the coarse-crushing region extends beyond the fine-crushing region a length approximately 8.2:.

'60 To simplify the process of transposing the de- 'veloped data of Fig. 6 to the arcuate case of v Fig. 1, construction lines may be drawn normal to the plane surface of crushing element 24 for successive increments of :1: along the surface; the intercepts-of these construction lines with the 5 and with the 31 inclined surfaces define the construction spans to be utilized in Fig. 7. These spans are identified as a-aa, bbb, c-cc, etc.

Referring to Fig. 7, the coarse-crush region 22 and the fine-crush region 23 will be recognized between the generally cylindrical surface of the crushing mantle and the complex surface of the jaw i6. Dotted lines II and II" indicate the the crushing surface of the mantle II. To develop the complex surface of Jaw l8, an average position of the crushing mantle ll (full line, backed by cross-hatching) is laid out for the crushing mantle surface, and radially extending construction lines are drawn for each increment of .1: along the periphery. The construction points defined by these increments are identified by the legends a, b, c', etc, The complex surface is then developed by laying out for each of the points a, b, etc., spans a'-aa', b'bb', etc. (taken directly from spans'ta-aa, b-bb, etc. of Fig. 6) along the radially extending construction lines passing through these points, as will be clear. To promote the rapid discharge of fine-crush material from the lower zone 23, I

prefer that, whatever the placement of the law with respect to the mantle, the lower jaw lip 23' (defining the lower limit of the fine-crush zone 23) shall be spaced from, or shall at least not substantially project (toward the drum axis) beyond an imaginary vertical plane representing a vertical tangent to the crusher mantle at the time (see dotted line H) of nearest approach to the jaw.

It will be seen that with the two-arc construction which I have described, crushing is accomplishedsubstantially in two stages. The first or coarse crushing zone is characterized by relatively wide divergence ofv the chamber walls, so that material crushed in this relatively wide region will break with an upward thrust (due to having provided a relativelylarge included angle dependent on the properties of the material to be crushed, so as to permit upward slippage of large particles). I ticles mixed with the larger sizes in this upper region will be agitated by the gyrating roll and, instead of being crushed in a mass together, will slip downward. This slippage and agitation tends to classify the materials as to size, allowing the finer particles to sift down to the lower or finecrushing zone, where each charge to be crushed fine may be reduced with a single stroke which crushes substantially the entire mass in this lower region. It is believed that single-stroke crushing in the lower region 23 may result from the low slippage inherent for a chamber having the relatively slight included angle which char- Although the change in crushing angles from the upper zone 22 to the lower zone 23 is shown to be, and has been implied as'being, quite abrupt at the intersection at the two substantially arcuate surfaces, it is clear that this transitional line may be rounded slightly in manufacture or that itmay be left to wear round in the course of use. According to another feature of the invention,

the sleeve means It, which serves .as a bearing support for thecrushing drum I2 on the eccen tric surface II, also serves as a partial anchor to remove'substantially all the purely rotational components of motion of the eccentric shaft l5. Thus, the motion of the crushing mantle Ii will be-substantially only eccentric, and the mantle I I may be said to be driven or supported by nonrotating eccentric means. Under heavy load conditions, however, and since the drum I2 is rotatable relative to the eccentric means, the increased localized friction between the drum l2 extreme lateral positions for eccentric throw of 7 s and sleeve means I; will be understood to be such At the same time, smaller paras to promote and to permit slight progressive rotation of the mantle ll. Under the more adverse load conditions, this slight rotation will be understood to provide a means of automatically evenly distributing wear over the entire exposed surface of the mantle l I.

In the form shown, the sleeve means I3 is effectively anchored against rotation by the action of an axially extending stop 26 carried by a frame member 1 and extending into a radially extending slot 21 in a flange 28 in the sleeve means l3 (see Figs. 3 and 5). If desired, a freewheeling roller 28 may be carried at the slotengaging end of the stop 26, to reduce friction and wear in the walls of the slot 21. It will be understood that the depth of the slot 21 should be suflicient to accommodate the full eccentric throw of the surface I4 without impeding such throw.

To reduce maintenance costs, I provide a plurality of removable crusher-plate elements on each of the swing jaws l6 and I1. In the form shown, each crusher plate is made up of two plate elements (30, 3| for jaw l6, and 32, 33 for jaw I1) set obtusely in two correspondingly obtusely inclined plate-receiving recesses 34, 35 (of jaw l6). Preferably, the lower edge of the lower recess 34 is acutely inclined with respect to recess 34, so that a single wedging action applied at the top edge of upper plate 38 may serve to secure both plates 30 and 3| to the jaw-plate holder Hi. This wedging action is shown to be supplied by adjustable take-up of bolt means 36 having a wedge-shaped head mating with the acutely-inclined upper edge of plate 30 and with the obtusely inclined upper edge of the recess 33. It will be clear that the structure described for the crusher-plate assembly constitutes not only an improvement over previous methods of mounting but also a means for readily interchanging parts, particularly those representing areas subjected to greater wear.

In order to relieve stresses due to abnormally high crushing efforts demanded by certain undesired contaminations of the material to be crushed or by other unanticipated load conditions, I provide novel resilient shock-absorbing means linking the swing jaws l6 and 11 to the butt end 38 of the stud resiliently carried by springs 31 is preferably formed with a generally spherical convex surface, for, a purpose which will be clear. To oppose the less frequently occurring and abnormally large transient forces, I employ a hydraulic absorber 38 securely mounted to the frame of the machine and having a piston 40. In the form shown, piston 48 is formed with a generally spherical concave end to receive the butt end 38 resiliently supporting the jaw l6. Safety-valve means 41 serve to relieve excessive pressures within the absorber 39, and a standard fitting 42 may be employed for replenishing the supply of hydraulic absorber fluid. A relatively weakly sprung link 43 may be used to avoid "chatter or transient separation of piston 40 from the butt 38. 7

It is clear that, aside from the function of protecting the crushing jaws, the frame, and the eccentric mechanism against excessive mechanical overload, the hydraulic absorbers may, depending upon the volume of fluid employed, serve the additional function of accurately positioning the swing jaws in accordance with the relative wear of crushing surfaces and in accordance with the desired flneness of crushed product. If permanent connection is made via the fitting 42 to a source of adjustable fluid pressure, the desired positions of crushing surfaces may be automatically maintained by simple adjustment of the fluid pressure, as will be understood. The generally spherical mating surfaces of butt 38 and of piston." may then serve to translate absorbent forces fromabsorber 38 to theswing jaw 16 for a number of possible positions of the swing law It.

In accordance with a further feature of the invention the sleeve means I3 is formed in two similar parts each of which is characterized by a generally annular bearing portion 44 and by a. side flange 28. The axial length of the bearing portions 44 is preferably such that when the flanges 28 are in abutment with the ends of crushing drum 12 the inner ends of the bearing portions 44 are slightly spaced, to provide an annular manifold 45 for the peripherally uniform conduct of lubricating fluid to the interfitting bearing surfaces of the eccentric cylinder I4 of the sleeve means l3 and of the drum l2. In the form shown, the supply of lubricant to the manifold 45 is effected by a drilled duct extending first axially, as at 46, and then radially, as at 41 into communication with the manifold 45. If desired, this lubrication may be effected continuously under pressure through a suitable feeding mechanism 48 terminating at one end of the shaft l5.

The lubrication process for the eccentrically thrown components is completed by means of an extraction system at both ends of the crusher drum for removing dust-laden or otherwise-contaminated lubricant. In the form shown, closely overlapping members 49-58 are supported respectively on the frame member 1 and on the drum l2 to define an annularly extending exhaust manifold for receiving used lubricant exuding from the main-bearing surfaces and from the eccentric-bearing surfaces of sleeve means l3. An exhaust line 5|, which i preferably maintained at reduced pressure, communicates with the exhaust manifolds at both ends of the machine for collection of used lubricant for possible filtration and recirculation under high pressure.

In accordance with a still further feature of theinventior'nsmooth operation of my machine is promoted by a balancing of the eccentrically gyrated mass with suitable counterweights or fly wheels 52-53 carried by the shaft at both sides of the machine external to the outboard bearings 9-l8. In the form shown,- both counterventional single-arc; crusher means ,that the same volume of crushing load may be handled in a machine needing less head-room clearance.

Wear of crushing surfaces may be more evenly distributed (1) by the automatic relatively slow rotation of mantle I I, in accordance with the load,

7 and (2) by simple interchanging or servicing of the jaw-plate areas most subjected to wear. The spring-and-hydraulic shock-absorbing mechanism relieves the cooperating parts of undue stresses, with a resultant prolonging of mechanical service.

I I have indicated how my novel shock-absorbing mechanism may, with suitable adjustment of hydraulic pressure in the cylinders 39. serve alternatively to take-up the mean positioning of the jaws l6 and I! with wear of their crushing surfaces or to position the jaws for a given fineness of crush. Further adjustments of the crushing surfaces for either of these purposes may be effected by suitable bearings for the pivot journals carrying the jaws lS-l'l. It will be understood that such adjustment may readily be made by bolting these pivot bearings through slotted ways (not shown) in the upper flanges of the side frame members 6---'!.

It will also be clear that the lubrication system described for the eccentrically thrown components may be utilized in part for eiilcient lubrication of the main outboard bearings 9-40. In the form shown, each of these bearings includes a feed duct 55 for clean lubricant and lubricant-sealing means 56 at the outer exposed end of the bearing. The inner ends of the bearings are then open to the annular exhaust manifold defined by the overlapping members 4950. With thisconstruction, the bearings may be fed with clean lubricant from the same high-pressure system and drained ofdirty used lubricant by the same exhaust system as has been described for the eccentrically thrown mechanism.

Although I have described my invention with particular reference to the preferred form shown. ,itjwill be understood that modifications may be made within the scope of the claims which follow.

i. In a crushing device, a generally cylindrical crusher drum, cylindrical means including an outer cylindrical surface wholly supporting said drum and over which said drum is rotatable, rotating eccentric means for imparting eccentric motion-to the axis of said cylindrical means, means holding said cylindrical means against rotation, the axis of rotation of said eccentric means being substantially horizontally disposed,

jaw means having a crushing side for coopera tion with said drum, said crushing side having two generally concave surfaces intersecting in substantially the same horizontal plane as the axis of 'rotation' of said eccentric means, the upper. of'said surfaces making a larger included angle with the periphery of said drum than the lower ofsaid surfaces, whereby the upperof said surfaces may cooperate with said drum to define a coarse-crush zone and the lower of said surfaces may cooperate with said drum to deaxially projecting stop member carried by said frame and engageable in a radially extending slot atone end of. said eccentric means. 7 v 3 In a crushing device, a generally continuously peripherally cylindrical crusher drum. cylindrical means including an outer cylindrical surface wholly supporting said .drum on a horizontal axis, said drum being free to rotate on said cylindrical supporting means, rotating eccentric means or imparting eccentric motion to the axis of said cylindrical means, whereby a.substantially vertical plane may be defined tangent to the outer surface of said drum at the location of maximum eccentric throw of said drum to one side thereof, means holding said cylindrical means against rotation, and relatively fixed jaw means supported in horizontally spaced relation with said one side of said drum and having a crushing side for cooperation with said drum, said crushing side having an upper generally concave surface making with the periphery of said drum a substantially constant first downwardly converging included angle, said crushing side also having a lower generally concave surface making with the periphery of said drum a substantially constant second downwardly converging included angle, whereby each of said concave surfaces may define with said drum essentially separate downwardly converging crushing zones, for the purpose described, the upper of said zones having a substantially larger effective included angle than the lower of said zones, the lower edge of said lower concave surface being for the most part spaced from and extending at most insubstantially through said plane.

4. In a crushing machine of the character indicated, a frame, a generally horizontally disposed cylindrical crusher drum, drum-supporting means, rotating eccentric means journalled jaw means on opposite sides of said drum,

whereby crushing may be effected alternately on opposite sides of said drum in an up-crushing zone and in a down-crushing zone, said jaw means on the side of the up-crushing zone comprising two adjacent concave crushing surfaces making with the periphery of said drum two different substantially constant downwardly converging eifective included angles having the same direction of convergence, the surface characterized by the larger of said included angles being above the surface with the smaller of said included angles, andsaid larger included angle having a maximum extent of 32, for the purpose described.

5. In a crushing device, a generally cy1indri.-

drum may creep around said sleeve as necesby said frame, said eccentric means including sitated by wear and crushing pose described.

6. In a crushing device. a frame, rotating eccentric means rotatable on an axis supported load, for the puran eccentrically thrown generally cylindrical surface, sleeve means extending substantially over said surface, a crusher drum carried by said sleeve means, jaw means on one side of said drum and defining with said drum a crushing chamber, and rotation-resisting means carried by said frame for arresting rotational motion of said sleeve, whereby substantially only eccentric motion is imparted to said drum, and further whereby rotational motion of said drum is proportional to the crushing load encountered by said drum in the crushing chamber.

7. In a crushing device, aframe, rotating eccentric means rotatable about an axis supported by said frame, said eccentric means including a generally cylindrical drum-supporting means, a crusher drum supported wholly on said drumsupporting means, and rotation-resisting means cooperating between said frame and said drumsupporting means for resisting rotational motion of said drum, forthe purpose described.

8. In a crushing machine, a frame, a crusher drum, rotating eccentric means for impartin eccentric motion to said drum, sleeve means intermediate said eccentric means and said drum, said drum being wholly supported by said sleeve means, said sleeve means having a radially extending flange with a radially extending slot at one end of said drum, and means carried by said frame and engaging said slot for locking said sleeve means against rotation.

' CHARLES A. ADAMS.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 286,723 McDowell Oct. 16, 1883 434,786 Howland -1--- Aug. 29, 1890 896,547 James Aug. 18, 1908 929,177 Watt et a1 July 27, 1909 1,054,123 Hutchinson Feb. 25, 1913 1,574,142 Weston Feb. 23, 1926 1,578,948 Bakstad Mar. 30, 1926 1,972,096 Guest Sept. 4, 1934 2,044,653 Wettlaufer June 16, 1936 2,097,906 Wettlaufer Nov. 2, 1937 2,131,801 Gruender Oct. 4, 1938 2,147,833 Fahrenwald Feb. 21 1939 2,177,524 Gruender Oct. 24, 1939 2,204,024 Meinhardt June 11, 1940 2,231,491 Bousman Feb. 11, 1941 2,302,723 Symons Nov. 24, 1942 2,303,923 Fahrenwald Dec. 1, 1942 2,375,370 Krider May 8, 1945 2,383,457 Anderson Aug. 28, 1945 2,464,732 Traylor Mar. 15, 1949 FOREIGN PATENTS Number Country Date 429,473 Great Britain May 30, 1935 

